EP1172561B1 - Pompe avec accouplement magnétique - Google Patents

Pompe avec accouplement magnétique Download PDF

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Publication number
EP1172561B1
EP1172561B1 EP01116648A EP01116648A EP1172561B1 EP 1172561 B1 EP1172561 B1 EP 1172561B1 EP 01116648 A EP01116648 A EP 01116648A EP 01116648 A EP01116648 A EP 01116648A EP 1172561 B1 EP1172561 B1 EP 1172561B1
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EP
European Patent Office
Prior art keywords
pump
feed wheel
speed
set forth
drive member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP01116648A
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German (de)
English (en)
Other versions
EP1172561A3 (fr
EP1172561A2 (fr
Inventor
Hans Dipl.-Ing. Martin
Jürgen Dipl.-Ing. Bohner
Raimund Dr. Ing. Rösch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Martin Hans
Schwaebische Huettenwerke Automotive GmbH
Original Assignee
Martin Hans
Schwaebische Huettenwerke Automotive GmbH
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Publication date
Application filed by Martin Hans, Schwaebische Huettenwerke Automotive GmbH filed Critical Martin Hans
Publication of EP1172561A2 publication Critical patent/EP1172561A2/fr
Publication of EP1172561A3 publication Critical patent/EP1172561A3/fr
Application granted granted Critical
Publication of EP1172561B1 publication Critical patent/EP1172561B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0069—Magnetic couplings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes

Definitions

  • the invention relates to pumps, in particular positive displacement pumps, for oil and also others Media, preferably liquids.
  • the invention relates to pumps that a Have a delivery volume limitation and / or a delivery volume adjustment.
  • a Have a delivery volume limitation and / or a delivery volume adjustment.
  • On preferred fields of application are land, air and Water vehicles, in particular cars and trucks.
  • Pumps with advantage also in other ways, for example to supply a press Pressure oil, can be used.
  • EP 0 994 257 A1 describes an external gear pump with an adjustment of the specific funding volume, i.e. Delivery volume / pump speed described.
  • the Adjustment is made by changing the length of engagement of two in engagement located gears.
  • one of the gears is mounted on a piston, pump pressure on one side and pump pressure on the other Side spring pressure.
  • EP 0 855 515 A1 a turbomachine in the form of an impeller pump with a magnetic coupling known.
  • the magnetic coupling is a function of a speed that with a Sensor is measured, adjusted to promote the coolant as needed.
  • the Adjustment is effected with an adjustment motor and a mechanical gear.
  • gear pumps for example external gear pumps and Internal gear pumps
  • oil pumps according to the invention form, two gears are in meshing engagement and form together with Walls of a surrounding housing a delivery space through which to pumping medium from a low pressure side to a high pressure side of the pump is promoted.
  • the low pressure side is with a pump inlet and the High pressure side connected to a pump outlet.
  • gear pumps In known gear pumps, one of the two gears of a gear wheel set stored by the pump housing.
  • the other gear is from one Rotary drive member is rotationally driven and for this purpose is non-rotatable with the Rotary drive member connected.
  • the rotary drive member supports this gear. in the generally the gear is torsionally rigid connected directly to the rotary drive member.
  • the rotary drive member is in turn rotatably supported relative to the housing. by virtue of of manufacturing tolerances, assembly inaccuracies and those occurring in operation
  • the rotary drive member "works" under loads relative to the housing. Corresponding also find unwanted movements of the gear wheels of the gear pump relative to each other instead, for example canting.
  • Displacement pumps especially gear pumps, generally have a system-specific constant specific delivery rate [delivery volume / delivery wheel speed] because the geometry of the displacement cells cannot be changed. You point a proportionality of the delivery rate over the speed, as long as the degree of filling of the Is 100%. In many applications, however, this proportionality is annoying and undesirable.
  • a press for example, there is one for rapid traverse high delivery quantity of pressure oil is necessary, however, in the final phase of the working stroke only high pressure is required and the demand for oil production drops to zero. Since the drive speed of such pumps generally remains constant in presses, creates a high pressure oil flow surplus, which with a Loss of energy flows back into the oil tank.
  • a gear pump is known from WO 00/29741, which supplies a Vehicle engine is used with fuel.
  • the gear pump is used as a Synchronous clutch formed magnetic clutch driven.
  • the two coupling halves the magnetic coupling are displaceable relative to one another in order to increase Pump speed to obtain a regulation of the pump pressure.
  • the US-PS 4,747,744 describes an internal gear pump, which also has a Synchronous clutch formed magnetic clutch is driven. Also from the JP 63113192 A is the use of a magnetic synchronous clutch for driving a Gear pump known.
  • a pump preferably a gear pump, via a Magnetic clutch driven.
  • the feed wheel closest to the rotary drive element in the power flow can hereinafter referred to as the first conveyor wheel, regardless of Rotary drive member are stored.
  • the first conveyor wheel there is no mechanical, in particular none positive drive coupling between the rotary drive member and the first Conveyor wheel. Possible, unavoidable frictional forces are considered neglected assumed.
  • the first feed wheel is relative to that Rotary drive element, apart from that caused by the magnetic coupling Drive coupling, freely rotatable.
  • a housing of the pump Form the rotary bearing of the first conveyor wheel.
  • the preferably further driven by the first conveyor wheel, the other combing the first conveyor wheel and forming conveyor cells is also expediently pivoted through the housing. It therefore forms one and the same rigid body, namely the housing, preferably a one-piece housing part, the pivot bearing for the first Conveyor wheel and also the pivot bearing for the other, second conveyor wheel.
  • the axes of rotation of the two feed wheels are therefore relative to one another in the pump according to the invention more precisely aligned than with a storage of the conveyor wheels on or on relative mutually movable bodies.
  • the engagement of the two feed wheels in one another can in particular no more or at least far less than in known pumps the change of loads acting on the rotary drive member are disturbed. It inaccuracies resulting from assembly are also reduced.
  • the Magnetic coupling acts between the rotary drive member and the first feed wheel Attenuator against the transmission of disturbances or irregularities.
  • the magnetic clutch is available as a hysteresis clutch or induction clutch or hysteresis Induction coupling designed.
  • the magnetic coupling has on its drive half or / and on their output half a magnetic rotating body from one permanent magnetic material.
  • the magnetic rotating body is preferably on one Soft iron attached as a carrier.
  • a rotating body of the other half of the coupling, with the magnetic rotary body causes the magnetic torque transmission, by means of Induction material or preferably by means of hysteresis material or Combination of hysteresis and induction material formed.
  • An induction material for example Cu or Al, can be one for a hysteresis rotating body Form inference device and a carrier.
  • a hysteresis and Induction rotary body is combined in such a hysteresis and Induction coupling but preferably also on a soft iron as a carrier appropriate. If the rotating body consists only of hysteresis material or only Induction material, a soft iron advantageously also forms the carrier or the inference device.
  • the magnetic coupling can be an end rotary coupling or, more preferably, one Central rotary coupling.
  • a combined face and central rotary coupling also provides a preferred embodiment.
  • a gear pump is preferably an internal gear pump or a External gear pump formed.
  • a gear pump can be formed in a particularly compact manner if the two coupling halves of the magnetic coupling are one Central rotary coupling or central and front rotary coupling form, in which the magnetic interacting, concentric rings that interlock Pump wheels surround the pump, preferably at a radial distance.
  • the combination of an internal gear pump with such a magnetic coupling advantageous.
  • the rotary drive member is formed by a drive shaft, the first one surrounds it Delivery wheel preferably the drive shaft.
  • Delivery wheel preferably the drive shaft.
  • the rotary drive member and the first feed wheel in the axial direction of the drive shaft can be arranged side by side.
  • the rotary drive member can in preferred alternatives Designs can also be a drive wheel, for example a gear of a gear transmission or a chain, belt or toothed belt wheel, which in this case is the first conveyor wheel preferably surrounds.
  • the first feed wheel and the second conveyor wheel on or on circular cylindrical outer surfaces of the housing, these bearing surfaces preferably surrounding one another.
  • the above Magnetic material rings of the magnetic coupling advantageously surround the two Storage areas for the conveyor wheels.
  • the invention is not limited to the field of gear pumps, but in Rotary drive for positive displacement pumps, preferably oil pumps, and basically for Pumps of any type can be used with advantage.
  • By driving torque over a magnetic coupling can be introduced into the pump Delivery volume limitation or a delivery volume adjustment or both in Combination can be achieved.
  • An external gear pump with delivery volume adjustment is from the EP 0 994 257 A1, to which reference is made by way of example with regard to this type of pump.
  • none of the Toothed gears are moved axially to a To obtain a delivery volume limitation and / or delivery volume adjustment.
  • the magnetic coupling is designed that when a predetermined speed of one drive half is reached Magnetic coupling is a design that can be transmitted through the magnetic coupling specified limit torque - in the following also simplified as Maximum torque designated - is reached. With a further increase in Speed of the drive half kinks the speed of the output half compared to that Speed of the drive half. It preferably remains after that Limit torque corresponding limit speed - more specifically, by design according to the specified speed - above that in operation Speed range of the drive half or up to a predetermined higher speed constant as good as this can be approximated due to the magnetic interaction can.
  • the maximum torque depends on the air gap between the magnetic interacting rotating bodies, the shape of the magnetically interacting Rotating body, the magnetically effective materials used and the dimensions the magnetically interacting rotating body, in particular the size of the surface that is covered by these rotating bodies of both coupling halves together, and one Radial distance of the overlap area from the coupling axis of rotation.
  • dimensioning and arrangement of the magnetic interacting rotating body becomes the maximum torque of the clutch and thus the maximum speed of the first delivery wheel of the pump by designing the Magnetic coupling specified.
  • Other influencing factors such as Changes in viscosity of the pumped medium, which the relationship between Influence maximum torque and maximum speed are in this consideration not even considered.
  • a delivery volume can also be limited by moving the delivery pressure-dependent magnetically interacting rotating body of the two coupling halves relative can be reached to each other.
  • One of the two coupling halves is preferably through the pump housing is displaceable relative to the other, preferably along the Axis of rotation, mounted in such a way that with a displacement relative to the other Coupling half that of the magnetically interacting rotating bodies of the two Coupling halves covered area or a distance between each other facing surfaces are changed in size. This changes automatically also the size of the limit torque.
  • a spring member or a spring damping member is the delivery pressure arranged counteractively as a reset element.
  • the magnetic coupling and the reset element are designed, for example, so that a Delivery characteristic is obtained in which the pump within a first Pump speed range or a rapidly growing delivery rate and / or Has delivery pressure, which or in a first approximation proportional to the speed of the Pump is quickly up to within a second, higher speed range Reaches a preset pump speed and regulates itself in this preset pump speed subsequent third, even higher speed range of the Drive half of the magnetic clutch again stronger than in the second speed range the pump speed increases or is essentially constant in the third speed range remains.
  • the reset element can in particular by means of springs connected in series can be set as desired.
  • a funding characteristic of the type mentioned above is used for Motor vehicles advantageous in which a pump according to the invention for the Lubricating oil supply is driven by the internal combustion engine of the motor vehicle the pump speed is therefore in a fixed relationship to the motor speed.
  • motor vehicles need in the lower engine speed range, d. H. Large amounts of oil immediately from the start. After reaching a predetermined engine speed and the associated Pump speed and pump delivery is based on the given Engine speed subsequent speed range no or no appreciable increase the delivery rate of the pump. After driving through this middle one Speed range, generally this is the main operating range of the engine, at higher engine speeds again require a higher oil production rate because with the higher Engine speeds are accompanied by higher centrifugal forces at the points to be lubricated, for example on the crankshaft.
  • On is formed by the series-connected control springs preferably installed under pretension so that it is hardly in the lower speed range gives way. If the preload force is exceeded at the transition between the lower and In the middle speed range, the soft first spring begins to compress until it reaches upper end of the middle speed range against the harder second control spring Stop comes to rest. If the speed is increased further, the Characteristic then determined by the harder second control spring.
  • the design of the clutch for a flattening of the speed increase of the output half compared to the drive half from a corresponding to the application Limit speed can be advantageous with a for the purpose of changing the Transfer characteristics provided adjustability of the coupling halves for Get involved.
  • the magnetically interacting rotating bodies of the magnetic coupling are preferred arranged together in the housing of the pump so that a temperature control of the Rotary body, preferably cooling, through the medium conveyed by the pump is obtained.
  • the mutually facing outer surfaces of the magnetically interacting rotating bodies face each other directly in the case of the preferred arrangement in the pump housing of the pumped Medium washed around.
  • the magnetic interacting rotating body together in the pump housing and each other are arranged directly facing, the outer surfaces of the rotating body only separated from each other by a thin film of the medium to be conveyed.
  • the several Delivery wheels not only in gear pumps but also in other inventive Pumps, for example worm wheel pumps or vane pumps, preferably from a rigid housing, preferably of a one-piece housing part, stored and not of bodies movable relative to one another, although the latter is not fundamentally should be excluded.
  • inventive Pumps for example worm wheel pumps or vane pumps, preferably from a rigid housing, preferably of a one-piece housing part, stored and not of bodies movable relative to one another, although the latter is not fundamentally should be excluded.
  • a rotary bearing of both rotary bodies of the magnetic coupling by the is advantageous Casing.
  • the rotating bodies of the magnetic coupling are preferably of the same Housing such as the one feed wheel or the multiple feed wheels rotatably.
  • the pivot bearing is advantageous due to a one-piece housing part.
  • the rotating body of the Half of the drive is secured against rotation with the rotary drive element, but for Pivot bearing connected by the housing with sufficient mobility.
  • a pump according to the invention cannot only be used as a Lubricant pump for the engine and / or an automatic transmission or Manual transmissions are used, they can also be used, for example, for oil promote hydraulic valve lash compensation and / or as a pump for one Valve timing adjustment can be used. Also use as a pump for an automatic transmission or a servo drive, for example a power steering or in a braking system is advantageous.
  • Figure 1 shows an internal gear pump in a cross section.
  • the internal gear pump has an inner rotor 5 with an external toothing 5a and an outer rotor 6 an internal toothing 6i, the one with their external and internal teeth Form the ring gear set.
  • the external toothing 5a has one tooth less than that Internal toothing 6i.
  • the inner rotor 5 and the outer rotor 6 are one in a pump chamber Pump housing 3 rotatably mounted.
  • the axis of rotation 6 'of the outer rotor 6 runs spaced in parallel, i.e. eccentric to the axis of rotation 5 'of the inner rotor 5.
  • Die Eccentricity i.e. the distance between the two axes of rotation 5 'and 6' is "e" designated.
  • the inner rotor 5 and the outer rotor 6 form a fluid delivery space between them.
  • This fluid delivery space is in delivery cells 7 which are sealed off from one another in a pressure-tight manner divided.
  • the individual feed cells 7 are each between two successive ones Teeth of the inner rotor 5 and the inner toothing 6i of the outer rotor 6 formed by two consecutive teeth of the inner rotor with 5 head or flank contact two successive, opposite teeth of the internal toothing 6i to have.
  • the conveyor cells 7 are increasingly larger in the direction of rotation D in order to subsequently move from the location slightest tooth engagement to the place of deepest tooth engagement again.
  • the Feed cells 7 that become larger form a low-pressure side 8 and the smaller ones becoming a high-pressure side 9.
  • the low-pressure side 8 is with a Pump inlet and the high pressure side 9 connected to a pump outlet.
  • Housing 3 are kidney-shaped, laterally adjoining the feed cells 7 Except slot openings. At least one opening covers conveyor cells 7 on the Low-pressure side 8 and at least one further opening covers conveyor cells 7 the high pressure side 9. In the area of the deepest tooth mesh and in the area of the The housing forms the least possible meshing between the adjacent ones Openings.
  • the pump receives its rotary drive from a rotary drive element which is actuated by a Drive shaft 1 is formed.
  • the drive shaft 1 is opposite the housing 3 guided by a pivot bearing 4.
  • the pump as Lubricating oil or engine oil pump to supply an internal combustion engine, especially the reciprocating piston engine with lubricating oil is the drive shaft 1 usually around the output shaft of a transmission, the input shaft of which Crankshaft of the engine is.
  • the drive shaft 1 can in principle also by a Crankshaft are formed immediately. Likewise, it can by a balance shaft for force balancing or torque balancing of the motor.
  • the inner rotor 5 is not seated torsionally rigid on the drive shaft 1, but is rotatable relative to the drive shaft 1 in the Housing 3 and rotatably supported by the housing 3. Since the outer rotor 6 is also relative the drive shaft 1 is rotatably supported in the housing 3 and rotatably supported by the housing 3, becomes a rotary bearing of the ring gear set 5, 6 independently of the drive shaft 1 by the same, at least in the storage area completely rigid housing 3 reached.
  • the conveyor wheels 5 and 6 running in meshing engagement can therefore in particular exact alignment relative to each other.
  • the ring gear set 5, 6 receives its rotary drive from the drive shaft 1 via a Magnetic coupling.
  • the magnetic coupling has two magnetically interacting ones Rotary body 14 and 15. These two rotating bodies 14 and 15 are ring bodies formed and accommodated concentrically surrounding each other in the housing 3.
  • the outer rotating body 14 is formed by magnetic material and has uniform its circumference distributed permanent magnets on an inner surface have alternating polarities N and S in the circumferential direction.
  • the Magnetic material rotating body 14 is made on the inner lateral surface of an annular body 13 Soft iron arranged and secured against rotation with the ring body 13, preferably completely firmly connected.
  • the ring body 13 takes those that occur during operation Powers up.
  • the magnetically interacting rotating body 15 is by a Hysteresis material formed.
  • a ring body 16 made of soft iron forms the carrier for the hysteresis material rotating body 15 and is secured against rotation with this, preferably firmly connected.
  • the hysteresis material rotating body 15 surrounds the ring body 16 and lies on the rotating body 14 with its outer surface facing directly. Between the two rotating bodies 14 and 15 the narrowest possible annular gap remains.
  • the magnetic material rotating body 14 and Ring body 13 form an outer ring and the hysteresis material rotating body 15 and the ring body 16 an inner ring of the magnetic coupling.
  • the magnets can instead the inner ring and the hysteresis material also form the outer ring.
  • the All versions of hysteresis material can be replaced by induction material or can be combined with induction material to create an induction coupling or hysteresis and Form induction coupling. Training only as a hysteresis clutch however preferred.
  • a Drive half of the magnetic coupling which is immediately non-rotatable with the drive shaft 1 is connected and extends up to the magnetic material rotating body 14 by one formed only rigid rotor body, which is also referred to below as a drive rotor becomes.
  • the drive rotor is in Figure 3 in a cross section and a longitudinal section shown individually.
  • the drive rotor has the shape of a ring pot with one inner sleeve body 11, the outer ring 13, 14 and a radial connecting web 12. The sleeve body 11 is pushed onto the drive shaft 1 and secured against rotation the drive shaft 1 connected.
  • the anti-rotation lock is made up of two opposite flats 2 of the drive shaft 1 and corresponding counter surfaces formed in the bearing body 1.
  • the drive shaft 1 forms in the seating area of the Sleeve body 1 thus a double, and the sleeve body 11 forms the corresponding Counterpart.
  • An outer lateral surface of the sleeve body 11 is circular cylindrical and extends from a free outer edge of the sleeve body 11 to directly to the floor, i.e. the connecting web 12, the ring pot-shaped Drive rotor of the magnetic coupling.
  • the inner rotor 5 is mounted on the housing 3 so that it can be rotated at a close distance.
  • the magnetic coupling is formed by a single, rigid output rotor, which is also is ring-shaped.
  • An integral part of the output rotor is the inner rotor 5th figure 4 shows the output rotor individually in a cross section and a longitudinal section.
  • the inner rotor 5 and the ring body 16 form the walls of the pot and are secured against rotation, preferably completely stiff via a connecting web 17 which the bottom of the pot forms, connected with each other.
  • the inner rotor 5 and the ring body 16 and the Connecting bridge 17 can be made from a single piece.
  • the output rotor is also the one-layer or multi-layer hysteresis material rotating body 15th
  • a particularly rigid and compact pump obtained in that the outer ring 13, 14 of the drive half and the Inner ring 15, 16 of the output half of the clutch surrounding the gear wheel set 5, 6 in the housing 3 are arranged.
  • the ring pot which by the drive half 11-14 Magnetic coupling is formed, takes the ring pot through the output half 15-17 the magnetic coupling and the inner rotor 5 is formed.
  • the connecting webs 12 and 17 are closely spaced.
  • the drive half 11-14 of the magnetic coupling and the output half 15-17 with the inner rotor 5 are about the common axis of rotation 5 'rotatable relative to each other.
  • the compactness of the pump also contributes to that the ring gear set 5, 6 surrounds the drive shaft 1; protrudes in the embodiment a shaft end of the drive shaft 1 through the ring gear set 5, 6.
  • the delivery chamber The pump delimits the connecting web 17 at the rear of the pump Fluid inflow and fluid outflow on the low pressure side and the high pressure side of the Pump are on the wall of the housing opposite the connecting web 17 3 embedded or incorporated.
  • Figures 5 and 6 show the housing 3. In particular, the compact and accurate, but easy storage and reception of the gear set 5, 6 and Magnetic coupling recognizable.
  • the Through hole is to the rear of the housing 3 towards a receiving hole 20 expanded for the gear wheel set 5, 6.
  • the receiving bore 20 is one Surrounding ring 22.
  • the retaining ring 22 is radial of two circular cylindrical Shell surfaces 23 and 24 and axially delimited by a rear end face.
  • the lateral surface 23 is concentric with the axis of rotation 5 'and the inner lateral surface 24 concentric to the axis of rotation 6 '.
  • the outer lateral surface 23 forms together with the Inner surface of the ring body 16, a rotary slide bearing for the inner rotor 5.
  • Der Ring body 16 is thus not only the carrier of the hysteresis material rotating body 15, but at the same time also bearing ring for the inner rotor 5.
  • the inner lateral surface 24 forms together with the circular cylindrical outer surface of the outer rotor 6 Rotary sliding bearing of the outer rotor 6, as is also the case with known internal gerotor pumps the case is.
  • annular space 21 In the housing 3 there is also an annular space 21 around the retaining ring 22 concentric to the axis of rotation 5 '.
  • the lateral surface 23 forms a radially inner one Delimitation of the annular space 21.
  • circular cylindrical, radially outer circumferential surface 25 forms an outer boundary of the Annulus 21 and a tread for the outer ring 13, 14.
  • the drive rotor of the Magnetic coupling is from the housing 3, namely on the outer surface 25, rotatably mounted.
  • the annular space 21 are in the assembled state of the pump Outer ring 13, 14 and the inner ring 15, 16 of the magnetic coupling relative to the housing 3 rotatably added.
  • the operation of the pump is as follows: The rotation of the drive shaft 1 around Rotation axis 5 'is transmitted 1: 1 to the drive half 11-14 of the magnetic coupling.
  • the Rotation of the magnetic material rotating body 14 is caused by magnetic flux Torque to the hysteresis material rotating body 15.
  • the inner rotor 5 With the hysteresis material rotating body 15, the inner rotor 5 is also driven in rotation.
  • the inner rotor 5 meshes with the outer rotor 6 in the manner known for internal gerotor pumps, so that the conveyor cells 7 already described at the beginning, which are located on the low-pressure side 8 enlarge and reduce on the high pressure side 9 again, are formed. That on the low-pressure side 8 sucked fluid is conveyed to the high-pressure side 9 and under conveyed higher pressure.
  • the delivery volume of the pump should be according to a preferred funding characteristic, initially from a standstill with the speed increases rapidly and remains constant after reaching a certain value stay.
  • the magnetic coupling is like this designed that a limit torque that it can transmit at engine speed is reached from which the demand for engine oil or lubricating oil flattens or even remains constant or at least no longer increases if the engine speed continues to increase becomes. Due to the design of a magnetic coupling to a predetermined maximum or Limit torque, the magnetic coupling is particularly suitable as Transmission link in the drive train of lubricating oil pumps for internal combustion engines or other uses of oil pumps in which the above Funding behavior is an advantage.
  • a delivery pressure-dependent can advantageously also be used Adjustment or regulation of the pump can be realized without in the ring gear set the pump to intervene.
  • a magnetic coupling can limit the torque by axially shifting the two magnetically interacting rotating body 14 and 15 changed relative to each other become.
  • the limit torque can be set.
  • the limit torque can be determined by means of a Slidable magnetic coupling even when mounting the coupling once and firmly adjusted or even just fine-tuned.
  • the same magnetic coupling can be used on this Way for pumps with different specific delivery volumes to the pure Delivery volume limit can be used. This is particularly preferred Limit torque of the clutch with self-regulation of the pump-magnetic clutch system set by feedback.
  • the physical control loop is shown schematically in FIG. 7.
  • the leader for the controller is the speed of the drive shaft 1.
  • This delivery pressure P forms the controlled variable for the controller by moving the delivery pressure P to the axially displaceable stored coupling half is placed. In the exemplary embodiment, this is the drive half 11-14.
  • the pressure of a Consumer such as the engine oil pressure
  • the sliding coupling half be placed to the pressure that will ultimately be used for the delivery volume adjustment the decisive factor is to use it as a controlled variable.
  • the drive half forms a sliding control piston.
  • the displacement position of the control piston is balanced between the Delivery pressure P and the spring pressure.
  • the spring 27 is at zero delivery preferably installed preloaded between the housing 3 and the control piston.
  • the pumping behavior of the pump can be very precise actual funding needs can be adjusted without adjusting the gears.
  • the delivery behavior on the one hand by appropriate design of the magnetic coupling as such, in particular the design for a limit torque through which Spring characteristic of the spring 27 and also by the initial displacement position, which have the two coupling halves in relation to each other when the pump is at a standstill of an optimal funding behavior.
  • the The maximum coverage for zero funding As indicated in FIG. 7, the overlap of the two magnetic material rotating bodies 14 and 15 in Pump standstill below 100%, based on the maximum coverage.
  • the pressure control can be replaced by a temperature control.
  • the Control piston is in this case by a temperature-dependent actuator replaced.
  • the temperature-dependent actuator is formed by an element that changes shape depending on its temperature.
  • the shape-changing element can be, for example, a bimetal spring or a Expansion element. There can also be several shape-changing elements Form actuator.
  • the shape-changing actuator can be in the pumped medium immersed or only thermally conductive connected to the housing, so that the Regulation in direct dependence on the temperature of the working medium or the Housing is done.
  • an advantage of the invention is that the single feed wheel or the several delivery wheels of a pump for a delivery volume limitation and / or - adjustment does not have to or need to be adjusted, such an adjustment in Combination with the installation of a magnetic coupling according to the invention advantageous be provided.
  • a gear pump for example, in addition to an adjustable or non-adjustable Magnetic coupling an adjustment of the specific delivery volume can be provided, for example by adjusting the engagement length of the gears External gear pump.
  • FIG 8 is the course of the torque over the speed of the rotary drive member applied to a test pump with a hysteresis clutch according to the invention.
  • the Magnetic coupling of the test pump has a limit torque of approximately 1.5 Nm designed that under the conditions of the test at a drive speed of about 700 rpm is reached.
  • the torque curve has one at the limit torque Bend and flatten out significantly after reaching the limit torque.
  • the slope From the limit torque, ⁇ 2 of the torque curve is advantageously in all Embodiments of the invention at most half as large as the slope ⁇ 1 before reaching of the limit torque.
  • the one transmitted by the clutch increases Torque no longer increases after reaching the limit torque, but instead remains constant as indicated by the dashed line.
  • the one for the torque is also qualitative with the course of the speed of the Output half of the magnetic coupling coincides, i.e. up to the limit torque Speed of the output half 1: 1 with the speed of the drive half and kinks at the limit torque obtained by design. Also applies to the speed curve, that the curve of the output speed after reaching the limit speed at most half as much should be as large as before the limit speed was reached. A smaller slope, ideally a zero slope is preferred.

Claims (15)

  1. Pompe, de préférence pompe volumétrique, qui présente :
    a) un élément de commande de rotation (1), qui est entraíné avec une vitesse de rotation, qui est fonction d'une vitesse de rotation d'un moteur de commande,
    b) un carter (3),
    c) une première roue d'alimentation (5), disposée dans le carter (3), qui est couplée à l'élément de commande de rotation (1) en vue de l'application d'un couple de rotation et qui forme, avec des parois du carter, seule ou en coopération avec une deuxième roue d'alimentation (6), un espace d'alimentation (7) qui présente un côté basse pression (8), relié à un orifice d'admission de la pompe et un côté haute pression (9), relié à un orifice de refoulement de la pompe
    d) et un accouplement magnétique (11 - 17), qui accouple l'élément de commande de rotation (1) à la première roue d'alimentation (5) en vue de la transmission du couple de rotation et présente une moitié commande (11 - 14), reliée de manière anti-torsion à l'élément de commande de rotation (1) et une moitié sortie (15 - 17), reliée de manière anti-torsion à la première roue d'alimentation (5),
    e) une limitation du volume d'alimentation de la pompe étant obtenue par l'accouplement magnétique (11 - 17),
       caractérisée en ce que
    f) l'accouplement magnétique (11 - 17) est un accouplement à hystérésis ou à induction et est prévu pour la transmission d'un couple de rotation limite, de sorte que déjà sans déplacement de l'accouplement (11 - 17), la moitié sortie (15 - 17), lorsque est atteinte une vitesse de rotation paramétrée à la conception, n'augmente plus ou augmente au moins plus lentement que la vitesse de rotation de la moitié commande (11 - 14), quand la moitié commande (11 - 14) dépasse cette vitesse de rotation paramétrée, la vitesse de rotation paramétrée étant plus faible qu'une vitesse de régime maximale de la moitié commande (11 - 14).
  2. Pompe, de préférence pompe volumétrique, qui présente :
    a) un élément de commande de rotation (1), qui est entraíné avec une vitesse de rotation, qui est fonction d'une vitesse de rotation d'un moteur de commande,
    b) un carter (3),
    c) une première roue d'alimentation (5), disposée dans le bâti (3), qui est couplée à l'élément de commande de rotation (1) en vue de l'application d'un couple de rotation et qui forme, avec des parois du carter, seule ou en coopération avec une deuxième roue d'alimentation (6), un espace d'alimentation (7) qui présente un côté basse pression (8), relié à un orifice d'admission de la pompe et un côté haute pression (9), relié à un orifice de refoulement de la pompe
    d) et un accouplement magnétique (11 - 17), qui accouple l'élément de commande de rotation (1) à la première roue d'alimentation (5) en vue de la transmission du couple de rotation et présente une moitié commande (11 - 14), reliée de manière anti-torsion à l'élément de commande de rotation (1) et une moitié sortie (15 - 17), reliée de manière anti-torsion à la première roue d'alimentation (5),
    e) la moitié commande (11 - 14) et la moitié sortie (15 - 17) étant mobiles l'une par rapport à l'autre et un couple de rotation limite, transmissible, de l'accouplement magnétique (11 - 17) étant modifiable, par ce moyen,
       caractérisée en ce que
    f) l'accouplement magnétique (11 - 17) est un accouplement à hystérésis ou à induction
    g) et une pression de pompe (P) et une force de rappel élastique, opposée à la tension de pompe (P), agissent sur la moitié commande ou la moitié sortie (11 - 14 ; 15 - 17), logées de manière mobile, dans un sens de déplacement.
  3. Pompe selon la revendication précédente, caractérisée en ce qu'un ressort (27) est prévu pour produire la force de rappel.
  4. Pompe selon l'une des revendications précédentes, caractérisée en ce que la pompe est une pompe à engrenages et la première roue d'alimentation (5) est une roue dentée et que la pompe comprend une deuxième roue d'alimentation (6), disposée dans le carter (3) et formée en tant que roue dentée, les roues d'alimentation (5, 6) étant en engrènement denté pour l'acheminement d'un fluide.
  5. Pompe selon la revendication précédente, caractérisé en ce que la pompe est une pompe à couronne dentée intérieure avec un rotor interne, qui forme la première roue d'alimentation (5) et un rotor externe, qui forme la deuxième roue d'alimentation (6) et une denture extérieure (5a) du rotor interne, qui s'engrène avec la denture intérieure (6i) du rotor externe, présente au moins une dent de moins que la denture intérieure (6i).
  6. Pompe selon l'une des revendications précédentes, caractérisée en ce que la première roue d'alimentation (5) est montée à rotation par rapport à l'élément de commande de rotation (1).
  7. Pompe selon l'une des revendications précédentes, caractérisée en ce que la première roue d'alimentation (5) est supportée à rotation par le carter (3).
  8. Pompe selon la revendication précédente, caractérisée en ce qu'une surface de palier (23), sur laquelle la première roue d'alimentation (5) est supportée à rotation, et une surface de palier (24), sur laquelle la deuxième roue d'alimentation (6) est supportée à rotation, sont formées par le carter (3).
  9. Pompe selon la revendication précédente, caractérisée en ce que l'une (23) des surfaces de palier (23, 24) entoure l'autre (24) des surfaces de palier (23, 24).
  10. Pompe selon l'une des revendications précédentes, caractérisée en ce que l'élément de commande de rotation (1) est un arbre d'entraínement et que la première roue d'alimentation (5) est montée à pivotement autour de l'arbre d'entraínement.
  11. Pompe selon l'une des revendications précédentes, caractérisée en ce que la première roue d'alimentation (5) est reliée à une bague de palier (16) de manière anti-torsion, de préférence rigide et la bague de palier (16) forme avec le bâti (3) un palier de roulement (16, 23) pour la première roue d'alimentation (5) .
  12. Pompe selon la revendication précédente, caractérisée en ce qu'une surface de palier, formée par la bague de palier (16), a un diamètre qui est supérieur à un diamètre extérieur de la première roue d'alimentation (5).
  13. Pompe selon l'une des deux revendications précédentes, caractérisée en ce que la bague de palier (16) entoure la première roue d'alimentation (5).
  14. Pompe selon l'une des revendications précédentes, caractérisée en ce que l'accouplement magnétique (11 - 17) comprend deux corps tournants (14, 15), interactifs magnétiquement, qui sont reçus en commun dans le carter (3), pour un refroidissement par le fluide à acheminer.
  15. Pompe selon l'une des revendications précédentes, caractérisée en ce que l'accouplement magnétique (11 - 17) comprend deux corps annulaires (14, 15), interactifs magnétiquement, qui s'entourent mutuellement et entourent la première roue d'alimentation (5), ainsi que, de préférence, aussi, la deuxième roue d'alimentation (6), si une telle roue est prévue.
EP01116648A 2000-07-13 2001-07-13 Pompe avec accouplement magnétique Expired - Lifetime EP1172561B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10033950 2000-07-13
DE10033950A DE10033950C2 (de) 2000-07-13 2000-07-13 Pumpe mit Magnetkupplung

Publications (3)

Publication Number Publication Date
EP1172561A2 EP1172561A2 (fr) 2002-01-16
EP1172561A3 EP1172561A3 (fr) 2003-01-02
EP1172561B1 true EP1172561B1 (fr) 2004-09-15

Family

ID=7648724

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01116648A Expired - Lifetime EP1172561B1 (fr) 2000-07-13 2001-07-13 Pompe avec accouplement magnétique

Country Status (5)

Country Link
US (1) US6544019B2 (fr)
EP (1) EP1172561B1 (fr)
JP (1) JP2002115670A (fr)
AT (1) ATE276439T1 (fr)
DE (2) DE10033950C2 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6949854B1 (en) * 2001-03-16 2005-09-27 Michael Schlicht Method and apparatus for a continuously variable-ratio transmission
US20060039815A1 (en) * 2004-08-18 2006-02-23 Allan Chertok Fluid displacement pump
JP2006187257A (ja) * 2005-01-07 2006-07-20 Daiyanitorikkusu Kk アミド化合物の製造方法およびアクリルアミド系ポリマー
CA2602531C (fr) 2005-04-05 2013-08-13 Magna Powertrain, Inc. Pompe a huile a couple limite pour dispositifs de transfert d'energie
TWI259247B (en) * 2005-11-01 2006-08-01 Sunonwealth Electr Mach Ind Co Fluid pump
JP4792342B2 (ja) * 2006-07-19 2011-10-12 日立オートモティブシステムズ株式会社 内接歯車ポンプおよびパワーステアリング装置
JP5064886B2 (ja) * 2007-05-21 2012-10-31 株式会社Ｔｂｋ ギヤポンプ
US20090035121A1 (en) * 2007-07-31 2009-02-05 Dresser, Inc. Fluid Flow Modulation and Measurement
CA2670247A1 (fr) * 2008-07-09 2010-01-09 Magna Powertrain Usa, Inc. Pompe avec embrayage radial pour ensembles de transmission de puissance
DE102009028154A1 (de) * 2009-07-31 2011-02-03 Robert Bosch Gmbh Zahnradpumpe
US8721267B2 (en) 2010-05-25 2014-05-13 Veeder-Root Company Submersible pump utilizing magnetic clutch activated impeller
DE102012214503B4 (de) * 2012-08-14 2017-10-12 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit verstellbarem Fördervolumen, insbesondere zum Verstellen einer Kühlmittelpumpe
DE102015213387A1 (de) * 2015-07-16 2017-01-19 Robert Bosch Gmbh Rotationskolbenpumpe
DE102016115368A1 (de) * 2016-08-18 2018-02-22 Eberspächer Climate Control Systems GmbH & Co. KG Förderanordnung zum Bereitstellen zweier voneinander getrennt geführter Mediumströme, insbesondere bei einem brennstoffbetriebenen Fahrzeugheizgerät
CN107084129A (zh) * 2017-06-28 2017-08-22 辽宁科技大学 一种安装在管道内的磁力驱动微型齿轮泵

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US4004412A (en) * 1974-12-20 1977-01-25 Chandler Evans Inc. Gas turbine engine fuel metering system
CH664052A5 (de) * 1984-07-12 1988-01-29 Landis & Gyr Ag Hysteresekupplung.
JPS63113192A (ja) * 1986-10-31 1988-05-18 Toshiba Corp ギアポンプ
JPS63113191A (ja) * 1986-10-31 1988-05-18 Toshiba Corp ギアポンプ
US4747744A (en) * 1987-01-09 1988-05-31 Eastman Kodak Company Magnetic drive gerotor pump
JP2669676B2 (ja) * 1988-12-06 1997-10-29 株式会社山田製作所 トロコイド型オイルポンプ
ES2187716T3 (es) 1997-01-22 2003-06-16 Eugen Dr Schmidt Bomba para liquido refrigerante regulable para automoviles.
WO1998042985A1 (fr) 1997-03-24 1998-10-01 A/S De Smithske Pompe a engrenages et a couplage magnetique
DE19736797A1 (de) * 1997-08-23 1999-02-25 Behr Gmbh & Co Geregelter Antrieb für einen Kraftfahrzeug-Lüfter
DE19847132C2 (de) * 1998-10-13 2001-05-31 Schwaebische Huettenwerke Gmbh Außenzahnradpumpe mit Fördervolumenbegrenzung
SE9803894D0 (sv) 1998-11-12 1998-11-12 Volvo Lastvagnar Ab Rotary displacement pump

Also Published As

Publication number Publication date
DE10033950C2 (de) 2003-02-27
EP1172561A3 (fr) 2003-01-02
DE50103599D1 (de) 2004-10-21
EP1172561A2 (fr) 2002-01-16
US20020068000A1 (en) 2002-06-06
ATE276439T1 (de) 2004-10-15
US6544019B2 (en) 2003-04-08
DE10033950A1 (de) 2002-01-31
JP2002115670A (ja) 2002-04-19

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